Indexing punch presses



Nov. 12, 1935. w. MERRILL ET Al.

INDEXING PUNCH PRESSES Filed Sept. 29, 1934 9 Sheets-Sheet l 9 Sheets-Sheet 2 Filed Sept. 29, 1934 NR. QN EN v. swam e nwm mmf t e RAUM u? f Im e a wm .n aw tl V/ b www@ MMNQC E O @u I :o

Nov. 12, 1935. w. L.. MERRILL Er Al. 2,021,077

` INDEX-.ENG PUNCH PRESSES Filed Sept. 29, 1954 9 Sheets-Sheet 5 Nov. 12, 1935. w. L. MERRILL ET AL INDEXI NG PUNCH PRES SES Filed Sept. 29, 1934 9 Sheets-Sheet, 4

IHS/ehbo Wilbur* L. ["le NOV. 12, 1935. W MERRlLL ET AL 2,021,077

INDEXING PUNCH PRES SES Filed Sept. 29, 1954 9 Sheets-Sheet 5 46/ 4 3 lfm MINIMUM f5;

p l n [Il Il Irl/1 11111111111111111/1 zie Inventors: Wilbur` L.. Merrill, Freclevlck .Fi her, b #m78 y Then" Attorney.

Nov. 12,1935. W, MERRlLL ET AL 2,021,077

` INDEXINGPUNCH PRESSES v Filed Sept. 29, 1954 9 Sheets-Sheet 6 wel Inventors:

/53 /63 Wilbur L. Merrill, l Y Frederigk E.Fshc:r,

by 04M er Attorney.

w. l.. MERRILL. ET Al.

INDEXING PUNCH PRESSES- 'l Filed septA 29. 1954 9 Sheets-Sheet '7 Nov. 12, 1935.

NOV- 12, 1935 w, L. MERRILL ETAL 2,021,077

INDEXING PUNCH PRESSES Filed Sept. 29, 1954 9 Sheets-Sheet 8 0 (D 47 Emmi i lIrwvezvwt@maz Wilbur` l.. Merrill, Frederick Fihc-:r b Wwf' y Then" Attorney.

Patented Nov. 12, 1935 UNITED STATES INDEXING PUNCH PRESSES Wilbur L. Merrill and Frederick E. Fisher, Scotia, N. Y., assignors to General Electric Company, a corporation of New York Application September 29, 1934, Serial No. 746,084 56 claims. (c1. 164-87) The present invention relates to indexing punch presses for performing a plurality of punching operations on a movably arranged Work piece. The Work piece may be in the form of a strip, a rod or a disk of metal or like material. During normal punching operation a plurality of perforations, notches, openings or deformations are provided consecutively at predetermined time intervals. From another viewpoint, the punchingl effects the removing, severing or deforming of material from a Work piece moved through the punch press at a denite speed so that the portions acted upon have a predetermined spacing on the Work piece. Such indexing punch presses are used, for example, in the manufacture of laminations for electrical machines. In this case annular disks or blanks are provided with a plurality of notches which usually are uniformly spaced apart. Such machines may further be used for removing or severing pieces from a straight, curved or helically wound strip of material at predetermined distances on the strip.

The present invention is of particular signicance in connection with indexing punch presses for punchingr annular or circular blanks. However, certain novel principles involved in the improved punch press may be applied to other kinds of presses. The terms punch and punching accordingly are used hereinafter in their broadest 3o (broader than commonly used) sense to denote both punch presses and shears, punching, shearing and deforming operations. A piece to be punched or sheared is hereinafter termed a blank and the piece -after being punched or sheared is termed a Work.

The general object of our invention is to pro- Vide an improved construction and arrangement of indexing punch presses whereby the time for punching a blank is considerably reduced. This is partly accomplished according toour invention by the provision of a flying punch or severing tool. By a yi'ng punch we mean a tool which is arranged to perform during operation a reciprocating motion, that is, an upward and downward movement or stroke and at the same time a n swinging motion somewhat like a pendulum. The last movement may be considered as a backward and forward or an oscillating or a shuttle motion. The provision of such a punch or severing tool permits the carrying out of the punching operation while the blank is moving at a denite, uniform speed. In the case of a disk to be punched, the disk may be rotated continuously at a uniform speed during the punching operation or, from another viewpoint, no rest period of the blank to be punched is necessary While the punch acts upon the blank.

For a better understanding of the feature just mentioned and other objects and features of our invention, `attention is directed to the following 5 description in connection with the accompanying drawings.

In the drawings we have shown an indexing punch press embodying our invention, which press may be used for punching laminations for 10 electrical machines.

Fig. 1 is a front view of the press;

Fig. 2 is a plan View;

Fig. 2a is a plan View of the machine table;

Fig. 3 is a diagrammatic view of the working 15 mechanism of the press;

Fig. 3a is a detail view of the blank thickness gauging mechanism;

Fig. 4 is a sectional View of the punch mechanism; 20 Fig. 4a is a detail vieW of the drive shaft for the punch mechanism;

Fig. 5 is a sectional view along lines 5--5 of Fig. 4;

Fig. (i is a sectional View along line 6 6 of a 25 universal coupling in Fig. 4;

Fig. 7 is a view along line 1 -'l of Fig. 4;

Fig. 8 is a perspective exploded view of a rotatable table and a key-holding and actuating mechanism of Fig. 7; Y 30 Fig. 9 is a detailiview of a blank-gripping and removing mechanism of Fig. 1;

Fig. 10 is a plan View of Fig. 9;

Fig. 11 is a detail view of a blank-feeding mechanism; 35 Figs. 12 and 13 are enlarged sectional views along lines |2-l2 and 1'3--l3 respectively of Fig.

Fig. 14 is a. detail view of a blank-raising device; 40

Fig. 15 is a sectional view along line l5-I5 of Fig.`14;

Fig. 16 is a sectional view along line |6-l6 of Fig. 14;

Fig. 17 is an exploded perspective view of the 45 punch oscillating mechanism;

Fig. 18 is a diagram comprising a plurality ofA curves indicating the movements and the operation of Various elements of the punch press;

Fig. 19 is an electric connection diagram of the 50 press, and

Fig. 20 is a diagram indicating the relation between the movement of the punch and the die.

The punch press shown in the drawings comprises the following mechanisms:- i*

1. A feeding mechanism for feeding a blank to a table of the punch press.

2. A locating mechanism for properly locating or positioning a single blank on` the table and checking the blank.

3. A mechanism for transporting the located blank to the punch mechanism.

4. A punch mechanism for punching the blank.

5. A mechanism for removing a work, that is, a punched blank, from the punch mechanism.

6. A mechanism for discharging the work from the table of the punch press.

'7. A power agency. m

The different mechanisms are driven by a power agency such as an electric motor and they are interconnected and correlated so that each mechanism performs a definite movement at a certain time during the operation.

In the following the-seven mechanisms are described in the order aforementioned 1. FEEDING MECHANISM The aforementioned mechanisms of the machine are supported on a machine frame comprising a base 25, and a table 26 (Fig. l) secured to the base by supporting members 2l. The feeding mechanism when viewed from the front of the machine is disposed at the right-hand end thereof. As its name indicates, it serves for picking up blanks from a stack of blanks and feeding them to the table of the machine. The blanks in the present instance are annular disks provided with a central bore and a key notch, into which a plurality of uniformly spaced openings have to be punched near the outer periphery.

The feeding mechanism comprises three essential elements: (a) a first element or blank swinging mechanism 28(Fig. 3) for picking a single blank or disk from a stack of blanks and placing it on the machine table, (b) a second element or stack raising mechanism 29 for properly supporting the stack of blanks and gradually raising the stack of blanks so that the upper blank of the stack is always at a substantially definite level, and (c) a third element or gauging mechanism 3|) fortgauging the blank on the table to insure that only a single blank has been placed on the table and to automatically bring the whole machine to a stop in case more than a single blank has been placed on the table. 'I'he stack of blanks is disposed in front of the right-hand portion of the table. y

(a) Blank swinging mechanism' The first element 28 (Figs. 3 and 11) ofthe feeding mechanism includes means for picking up a blank from the stack, lifting the blank away from the stack, swinging the blank over to a central portion of the table and lowering vthe blank and placing it on the table. The lifting and lowering of the blank is effected by means including a lifting and lowering cam 3| which has a cylindrical groove 55 with two depressions 32 at substantially diametrically opposite points. The swinging motion is accomplished by means including a swing cam 33. These two cams arel each cycle as will be more fully described hereafter. In order to prevent a blank from being held on the feed bell by residual magnetism, means are provided to push or release the blank from the magnets of the feed bell. AThe releasing means includes a releasing cam 38 on the cam shaft 34.

The first element of the feeding mechanism, which as pointed out above serves for lifting a blank, swinging it onto a central portion of the table and placing it thereon, is shown more in detail in Fig. 11. It comprises a support 39 which is secured to the machine frame by a weld 4D (Fig. 1). A bearing bushing or sleeve 4| is secured in a vertical bore of the support 39. An outer sleeve 42 is rotatably arranged within the bearing bushing 4|. The outer sleeve 42 may be rotated, more specifically, turned back and forth, by a gear segment 43 secured to its lower end by a set screw 44 and a key 44a. The gear segment 43 meshes with another gear segment 45 (Fig. 3), which latter forms the end of one arm of a bell crank lever 46 supported on a fulcrum pin 47. The other arm of the bell crank `'lever carries a roller 48 engaged yin a cylindrical groove of the swing cam 33. From aconsideration of Fig. 3 it can be clearly seen that during rotation of the swing cam 33 the gear segment 45 of the bell crank lever is turned or swung back and forth, causing a similar swinging movement of the outer sleeve 42. The thrust of the outer sleeve 42 and other parts connected thereto is taken up by a ball bearing 49 (Fig. 11) resting on a recessed portion of the upper end of the support 39. An outer casing 50 resting on the thrust bearing 49 is secured to the upper end of the outer sleeve 42 by means of a set screw 5|. An inner sleeve 52 is slidably arranged within the outer sleeve 42 and forms a part of the means for lifting and lowering the feed bell 35. The lower end of the inner sleeve 52 projects'beyond the lower end of the outer sleeve 42 and is provided with a grooved guide ring 53 securely fastened thereto. The lifting and lowering of the intermediate sleeve 52 is accomplished by the lifting and lowering cam 3 I, as best shown in Fig. 3, through a lever mechanismcomprising a lever 54 which has one end guided in the cylindrical groove 55 of the cam 3|, and another end held on a fulcrum 56. An intermediate point of the lever 54 is connected by a. link 5'| to the left-hand end of a lever 58 held on a fulcrum 59 and provided with a forked end or yoke 60engaging the guide ring 53 through pins 6|.

When during operation the lever 54 is forced down into one of the depressions 32 of the cylindrical groove 55 it effects downward movement of the link 51 and through the lever 58 upward movement of the intermediate sleeve 52. As the depression 32 passes the lever 54, the latter is moved upward and causes upward movement of vthe link 51 rand downward movement of the guided by a bushing 63 secured in a bore of said sleeve 42. The bushings 63 and 63EL hold the outer and inner sleeves in concentricallyspaced relation to reduce friction between them during relative movement thereof. The feed bell 35 is pivotally connected to the ends of two levers 64 and 65. The latter are supported by pivots 66 and 61 respectively on side walls 68 of the outer casing 58. The right-hand ends of the levers 64 and 65 project into the casing 58 and are secured to the inner sleeve 52 through the intermediary of a square bushing 69 (Fig. l2). The levers 64 and 65 have forked ends or yokes 10 which engage side walls of the bushing 69 and are secured to said side walls and the inner sleeve 52 by means of screws 1| and buttons 1|a. The inner sleeve 52 and the square bushing 69 have a recess 12 intermediate the connections between the levers 54 and 65 (Figs. 1l and 13).

As stated above, means are provided to release, strip or push a blank from the bell 35 against the residual magnetism of the lifting magnets 36. These means include a lever 13 which has an intermediate point secured by a pin 14 to the side walls 68 of the outer casing 50. A plate or ring 15 made of non-magnetic material and centrally disposed in the lower portion of the feed bell 35 is connected to the forked end or yoke (Fig. 11) of the lever 13 by means of two adjustable links 16. The right-hand end of the releasing lever 13 projects through the aforementioned slot 12 in the inner sleeve 52 into a recess 11 of a push or releasing rod 18 disposed within the inner sleeve. The push rod 18 is concentrically spaced in the inner sleeve and held in spaced relation by short guide bearings. One of them is shown with respect to the upper end. It comprises a short bushing 19 of suitable bearing metal secured to the inner surface of the inner sleeve 52. The lower end of the releasing rod 18 projects through a guide bushing 80 which latter is secured in the bore of an ear 8| of the machine frame. The releasing rod 18 is actuated by the releasing cam 38 through th'e intermediary of a lever 82 which latter is held on a fulcrum 83, as shown in the perspective View of Fig. 3. The left-hand end of the lever engages a cylindrical groove in the releasing cam which groove has two depressions 84 similar to the depressions 32 of the cam 3|. The right-hand endof the releasing lever 82 has a forked portion or yoke 85 with pins 86 projecting into the grooveof a grooved ring 81. The connection between the lever 82 and the push rod is similar to the one between the lever 58 and the inner sleeve 52.

During a complete revolution of the releasing cam the push rod is moved down and up twice. One such down and upward movement is necessary to push a blank from the magnets when the latter are located directly over the table and the other down and upward movement is necessary to permit down and upward movement of the bell when the latter is located over the stack of blanks. The down and upward movement of the inner sleeve 52 and the releasing or push rod 18 may be the same when a blank is picked from the stack of blanks, whereas the push rod 18 is moved up somewhat further than the inner sleeve 52 while the feed bell 35 delivers the blank to the table to cause the plate 15 Within the bell 35 to push a blank away from the magnets. Thus, the arrangement may be such that no relative movement between the push rod and the inner sleeve takes place during the picking operation, whereas a relative movement takes place during the releasing operation.

curve 93.

A spiral spring 88 with a ring 89 thereon is provided on top of the grooved ring 81 on the push rod to act as a compensator during upward movement of the push rod 18. This is to enable a certain amount of resilience in the action of the stripping mechanism. To summarize the operation of the first element of the feeding mechanism, the swing cam 33 during a single revolution of the cam shaft 34 causes swinging movement of the feed bell 35 from the stack to the table and back to the stack. While the feed bell is located above the stack the lifting and lowering cam 3| causes through the lever mechanism 54, 51, 58, the inner sleeve 52 and the levers 64 and 65 downward movement of the bell and thereafter upward movement. At the same time the releasing cam 38 causes a similar movement of the releasing plate 15 through the lever 82, the releasing rod 18, the lever 13 and the links 16. Similar movements of the releasing plate 15 take place while the bell is swung onto the table to place the blank thereon with the difference, however, that the push rod together with the lever 13 is moved relatively to the inner sleeve and the levers 64 and 65 respectively to cause releasing of the blank from the feed bell 35.

The operation, particularly the cooperation of the different parts of the mechanism and their (zo-relation can be better understood from a consideration of thediagram in Fig. 18, showing one cycle of the operation of the different elements. The shaded area defined by the curves indicates the working strokes, that is, the strokes during which actual work is performed. 'The curve 90 illustrates the pick up operation. It begins at 90 degrees of the cycle and ends at 150 degrees. The actual picking or lifting of a blank takes place at the lowest point of the curve, that is, at about 115 degrees of the cycle. Thus, between 90 and 115 degrees of each cycle the feed bell is lowered onto the stack to receive a blank and between 115 and 150 degrees the feed bell with the blank is lifted from the stack of blanks. The curve 9|, indicated below the curve 90, represents the movement of the releasing mechanism which is substantially the same as that of the lifting mechanism. In other words, during the picking these two mechanisms move in synchronism as pointed out above. Shortly after the termination of the picking-up operation, the feed bell is swung onto the table. The swingmovement or stroke from the stack to the table is indicated by the curve 92. It begins at about 165 degrees of the cycle and ends at about 315 degrees. During this movement the blank moves in a horizontal plane. A few degrees of a cycle after the blank has been swung onto the table, in the present instance at about 320 dgrees, there begins the dropping and releasing operation, during which the blank is lowered onto the table. The lowering and raising movement is indicated by the The releasing mechanism is simultaneously operated as indicated by the curve 94. As clearly shown, the height of the curve 94 is somewhat greater than that of the curve 93, causing a relative movement between the lowering and the releasing mechanism, more specifically between the feed bell 35 and the push plate 15, whereby the blank is pushed off the feed bell. After lowering and releasing a blank, the bell is lifted, reaching its upper level at about 360 degrees, whence a new cycle begins. The feed arm is swung back to the stack. Its movement, as indicated by the curve 95,-begins at zero degrees and ends at about ninety degrees.

The arrangement for controlling the electric y circuit for the feed bell magnets is indicated in Fig. 19. In the present instance the feed bell. 35 has magnets, each of which has a coil 91. coils of the six magnets are connected in series to a source of energy 98. The magnet circuit is automatically closed and opened by a cam 99 secured to the cam shaft 34, which cam act-uates a contact making and breaking member `l 00. The cam 99 for closing and opening the circuit for the feed bell magnets and the contact making member |00 which includes a roller |00a riding on the cam surface of the cam 99 are also shown in Figs. 1 and 3.

(b) Stack raising mechanism The second mechanism 29 of the feeding mechanism as stated above, serves for supporting and gradually raising a stack of blanks so that the upper blank of the stack is always at a substantially definite level to be picked up by the feed bell. Thisv mechanism which may be termed the stack raising mechanism comprises a frame |0| diagrammatically indicated in Fig. 3 and shown more in detail in Figs. 14 and l5. The frame I0! has a' bottom plate |02 provided with a vertically disposed bushing |03 for guiding a feed screw |04. Provided between a shouldered portion |05 of the feed screw and the bottom |02 of the frame is a thrust bearing shown as Van ordinary ball bearing |00 for taking up the thrust of the screw and other elements connected thereto. The feed screw |04 is surrounded by a spindle which comprises two halves |01 andl |08 forming portions of a cylinder and being concentrically arranged with and spaced from the feed screw. The two halves |01-and |08, as clearly indicated in Fig. 16, are spaced apart to dene vertical passages |09 and 0 between their adjacent edges. The lower ends of the two halves 01 and |08 are held in position by means of a ring fastened to said halves by screws ||2 (Figs. 3 and 15). The ring as clearly indicated in Fig. 3, projects through openings |I3 in side walls H4 of the frame |0|. The upper ends of the two halves |01 and |08 are held apart by a cap ||5 (Fig. 14) each half being secured to the ctw by' a screw ||6. This cap has a central bore provided with a bushing ||1 which forms a bearing for the upper end of the feed screw. The feed spindle comprising the halves `|01 and |08 is provided with means for keeping the key notches of the blanks properly aligned. To this end one of the halves, in the present instance the half |08 (Fig. 16), has a key |8 fitting into the key notches of the blanks. The blanks are supported by a chuck ||9 arranged to be gradually raised by the spindle and when reaching a certain level or upper end position to be dropped into a lower end position. The chuck comprises two halves |20 and |2|. Each half has two side walls |22 and |23 held together in spaced relation at their base by a bracket |24, and in addition by an upper bracket |25 and an end plate |25a suitably secured to the side plates. A releasing dog |26 is held between the side walls |22 and |23 of each half by a pivot The |21. Pivotally connected to a downward projection of each dog is a jaw |28 comprising an outwardly projecting member v|29 guided in inner recesses of the side plates |22 and |23, and a somewhat cylindrically shaped member |30 pro- 5 jecting through the slots |09 and ||0 respectively of the spindle. The member |30 has an internal screw-threaded portion |3| fitting the thread of the feed spindle |04. f

In Fig. 14 the chuck is shown in its upper end 10 position in which a nose |32 of each dog is engaged by an adjustable screw |33 whereby the lower portions of the dogs are forced outward and effect disengagement of the threaded jaw portions |3| with the thread of the feed screw 15 |04. AThe two halves of the chuck are united by a lower ring |34 secured to the lower brackets |24 and anl upper ring |35 suitably secured to the upper brackets |25. From the drawings it will be readily seen that the rings |34 and |35 to- 20 gether with the inner portions of the brackets |24 and |25-are disposed within the annular space dened between the feed spindle and the feed screw. The arrangement is such that the rings |34 and |35 slidably engage the inner sur- 25 face of the feed spindle halves |01 and |00. The

threaded portions 3| of the two halves of the chucks during operation engage the feed spindle and the end pieces of the members |30 are guided between the brackets |25 when said members 30 are moved radially outward, that is, released from their engagement with the feed screw.

The upper end of each dog has two depressions |35 adjacent each other. At one time a ball |31 is pressed into one of the depressions by 35 the action of a compression spring |38 to keep the dog in a iiXed position. The chuck has been shown in Fig. 14 with the threaded members |3| out of engagement with the feed screw. The disengaging, as stated above, is effected by the o dogs |20 and the screws |33. As this upper end, position is reached, the chuck drops instantly down into its lower end position to receive another stack of blanks. Means are provided at the lower end of the stack operating mechanism 45 to absorb inertia or shock from the dropping chuck and to effect engagement between the chuck and the feed screw. The shock of the falling chuck is absorbed by leather cushions |39 which are flexibly mounted on the frame |0| 50- by means including a bracket |40 on each side and bolts |4| and |42 with springs |43 and |44. The shock absorbers engage outer portions of the side walls |22 and |23 during the dropping of the chuck whereby the leather cushions |39 are 55 forced outward and absorb the inertia of the dropping chuck.

The mechanism for effecting re-engagement of the chuck with the feed screw comprises two dog actuators |45 and |40, one for each half 60 of the chuck. The lower ends of the dogs of the chuck are engaged by the dog actuators |45 and |46 when the chuck has been dropped into its lower end position. Each actuator is mounted on a carrier |41 slidably arranged in a slot |48 65 and forced radially inward by a compression spring |49. Secured to the lower side of each carrier is a roller |50, which latter engages a; cam |5|. The cam |5|, is secured to the spindle and rotates slowly therewith. During rotation 70 the cam forces the carriers |41 together with the actuators |46 slowly outward and also permits slow inward movement of the carriers and actuators whereby the latter cause inward movement of the lower ends .of the dogs and gradually Cil effect engagement between the threaded portions |3| of the chuck members I 30 and the feed screw.

During each cycle of the operation of the machine the feed screw is turned a certain angle to lift the stack of blanks an amount equal to the thickness of a single blank. This is accomplished by means including a ratchet or ratchet wheel |52 secured to the lower end of the feed screw by a nut |53. The ratchet is turned by a pawl |54, which latter is secured to a disk |55 loosely arranged on the feed screw shaft intermediate the ratchet wheel |52 and the bottom |02 of the stack frame. The pawl |54 is actuated through a link |56 including an adjustment |51 and being connected by a pivot |58'to one end of a link |59 carrying a roller |60 which latter engages a cam |6|. The roller |60 is secured to the link |59 by a pivot |62. The cam |6| which may also be in the form of an eccentric is secured to the lower end of the cam shaft 34. The ratchet wheel together with the feed spindle is prevented from turning backward while the pawl is moved out of engagement with the ratchet wheel by means of a one way lock latch |63, secured to the stack frame by a fulcrum |64 and held in engagement with the ratchet wheel by a compression spring |65 (Fig. l5) The link |59 carrying the roller` |60 is connected at one" end to a fulcrum |65, and the other end of said link is connected to a tension spring .|61 for biasing the roller |60 against the eccentric or cam |6|. During operation,'rotation of the cam |6| causes turning movement of the link |59 about its fulcrum |66 (Fig. 3) whereby the link |56 with the pawl |54 is pushed towards the ratchet wheel and effects turning thereof. The link |59 is slotted at one end and provided with a pivot pin |58a to permit stroke adjustment of the ratchet. The amount of the turning movement may be varied by changing rthe adjustment |582, depending upon the thickness of the individual blank. Thus, if under certain conditions the pawl moves the ratchet wheel one tooth during a single revolution of the eccentric 6|, thereby raising the stack of blanks to maintain the upper disk at a definite level, the adjustment has to be varied thereafter to push the ratchet wheel two teeth ahead during a single revolution if blanks of twice the thickness than before are to be raised.

The blanks are supported on the stack-raising mechanism by a plate |68 having a layer or cover of felt |6811 and being secured to the end plates |25a of the chuck. The provision of the felt cover |68a furnishes a measure of resilience and also facilitates the picking of the last blank. The picking of individual blanks is facilitated or, from another viewpoint, the picking of more than one blank from the stack is substantially prevented by the provision of stack-holding magnets |69 (Figs. 2 and 1l). The pole shoes of the magnets have knurled surfaces |693, as indicated in Fig. 2. In the present instance we have provided four stack-holding magnets. Pairs of magnets are secured to the ends of flat springs |69f, which latter are suitably supported at the upper ends of two holding rods |6913. The rods |69b have lower ends held on pivots |69C. Each magnet has an energizing coil |6911. are connected in series (Fig. 19) to the electric source or power line 98.

(c) Gaugz'ng mechanism forms the third element of the feeding mecha- The coils |69d nism serves for checking the operation of the feeding mechanism to insure that a single blank and not two or more blanks have been placed on the table. To this end means are provided for checking a condition, in the present instance the thickness of a blank or blanks placed on the table by the feeding mechanism. These means include a gauging spindle which is moved on the blank or blanks placed on the table, and means responsive to the movement of the gauging spindle for automatically disconnecting the electric circuit of themachine in response to an excessive thickness or like condition of the blank or blanks placed on the table.

The electric circuit (Fig. 19) includes a switch member |10 held closed by a relay |1|. 'I'he relay has a magnet coil |12 connected to a-battery or like source of electric energy |13. The coil circuit is closed by a photo-electric cell |14, which lattery is exposed to a source of light |15. ,As long as the light from the source |15 strikes the photo-electric cell |14, the circuit for coil |12 is energized and the switch member |10 accordingly is held in closed position. Arranged intermediate the source of light |15 and the photo-electric cell |14 is a movable member or diaphragm -A `if|"l6 which is moved by a gauging spindle a distance depending upon the thickness of the blank or. blanks placed on the table by the feeding mechanism. In case more than one blank is placed on the table or when a blank is faulty, that it, its thickness exceeds a certain value, the diaphragm |16 is moved sufficiently to interrupt the light radiated from the source |15 towards the cell. This causes automatically opening of` the switch 10, thus interrupting the electric crcuit and bringing the machine to a stop.

The mechanical construction of the gauging means, as shown in Fig. 3 and more in detail in Fig. 3a, comprises a cylinder or sleeve |11 for accommodating a gauging spindle |18. Anut or nuts |19 are screwed onto the upper end of the piston and bear against the end face of the cylinder |11. A compression spring surrounds the lower end of the spindle and bears against the end face of the cylinder |11 and a gauging plate |8|, forming a part of the spindle. 'Ihe cylinder is rigidly secured to one end of a ,lever |82, whose other end is supported on a fulcrum |83. An intermediate portion `of the lever |82 is pivoted to a roller |84, which latter bears against the cam surface of a gauging cam |85. The cam |85 is secured to the cam shaft l34. The roller |84 is held in engagement with the cam |85 by a compression spring |86. The diaphragm |16 is secured to the right-hand end of an arm |81. This arm projects through a longitudinal slot |88 (Fig. 3) of the lever |82 and is connected to the lever by a pivot |89 near the cylinder |11. The left-hand vend of the arm |81 projects through a slot |90 of the'cylinder (Fig. 3a) into a recess |9|`of the spindle |18. l Y

During operation, rotation of the gauging cam |85 effects downward turning movement of the lever |82 about its fulcrum |83 through the intermediary of the roller |84 which, as pointed out above, is pivoted to the lever and held in engagement with the gauging |85. The latter has two downwardly projecting lips l92 and 93 (Figs. 3 and 3a).

the desired thickness has been placed c be table. As the first downward projecting np 58 of the cam |85 comes into engagement with the roller, the latter together with the levez" |82 are forced downward a distance sufficient to bring Let us assur-ne that a single blank of l the gauging plate |8| of the piston into engagement with the upper surface of the'blan'k. During further rotation of the cam |85 the lip |03 comes into engagement with the roller |84, causing further downward turning movement of the lever |82. As the spindle |18 is prevented from further downward movement, it remains at rest but permits downward movement of the cylinder |11 under compression of the spring |80, thus effecting a relative movement between the cylinthe effect that the diaphragm |16 is moved into the path of light radiated from the source of light |15 towards the cell |14. The diaphragm thereby interrupts the beam of light, to the effect that the electric circuit is opened as described above.

2. LocA'rINc MEcHANrsM Each blank placed on the table by the feeding mechanism has a central bore with akey notch. The locating mechanism comprises means for properly locating, centering or positioning the blank on the table so that its key notch is in a denite position with relation to the table. This mechanism comprises a centering member or plug 200 (Fig. 3) which has a lower cylindrically shaped portion 20| and an upper conically shaped portion 202 provided with a' key 203 whose upper part is tapered. The plug 200 is normally disposed within an opening 204 (Figs. 2 and 2H) in the machine table and is fastened to the upper end of a rod 205, which latter is guided in bearings 206 and 201 (Fig. 1) suitably secured to -the machine frame. The locating plug 200 together with the rod is pressed in downward direction by a compression spring 208 surrounding an upper portion of the rod and disposed between a shoulder of the rod and a fixed guide member 209` forming a part of the machine table. The downward movement of the rod 205 by the action of the compression spring 208 is limited by a collar 2 0 secured to the rod above the lower guide bearing 206. Adjacent the lower lend of the rod 205 is the right-hand end of a lever 2|| which has an intermediate point supported by a fulcrum 2 |2 and a left-hand end provided with a roller 2|3 engaging an upper portion of a cam 2 |4 having a cam surface 2|5. Clockwise turning movement of the lever 2|| which may be termed locating lever is limited by an abutment 2|8 (Fig. 1l secured to a post 2|9 -on the machine frame. During operation, rotation of the cam 2|4 effects downward movement of the left-hand end of the locating lever 2| as soon as the roller 2 |3 on the lever comes into engagement with the cam surface 2|5.Y This effects upward movement of the right-hand end of the locating lever 2| whereby the rod 205 is forced upward and the member 200 is moved out of the hole in the machine table into the bore of a blank placed on the table. It is important to note that the blank is placed on the table by the feeding mechanism substantially in the position desired. The locating mechanism may effect merely a slight turning movement of the blank in either direction to assure accurate positioning of the blank on the table. The conical portion 202 with the tapered portion of the key 203 of the locating plug 200 facilitates the positioning of the blank. The plug 200 is moved upward until the cylindrical portion 20| with the 5 corresponding key portion 203 thereon projects into the bore and key notch of the blank to be located whereby the -placing of the blank by the 'feed mechanism is corrected and the blank is xed in its position. l0

The operation of the centering mechanism is shown in the diagram of Fig. 18 by a curve 220. The locating or centering member or plug 200 is moved upward, that is, above the table, at about 210 degrees of the indicated cycle and the plug 15 200 is moved down into the opening of the table at about 360 degrees, thus remaining above the table for approximately degrees of the complete cycle.

In the preceding section it was pointed out that 20 a blank is dropped onto the table under the action of the releasing mechanism at about 340 of the cycle. The locating plug is above the table while a blank is dropped thereon, so that the blank is located instantly. The action of locat- 25 ing, that is, the downward movement or dropping of the blank on the raised, locating plug, is facilitated by the conical shape of the plug and its key.

From a consideration of the curves 90, 9|, 92, 96, and 220 in Fig. 18 it is apparent that the han- 30 dling of an individual sheet by the feeding and locating mechanisms takes place during a single cycle of operations.

3. TRANsPoR'rING MEoHANIsM The blank or blanks are placed on the righthand portion of the table if -viewed from the front of the machine (Fig. 1) by the feeding mechanism and located, positioned or centered by the locating mechanism. The punch mechanism is dis'- 40 posed on a central portion of the machine and includes a movable or rotatable table located adjacent the aforementioned stationary table 26. The blank has to be moved from the centered position on the stationary table onto the rotatable 45 table of the punchmechanism. This action is accomplished by the transporting mechanism. The movement is eiected by the cam 2|4 which also actuates the locating mechanism. The cam 2|4, which accordingly may be termed locating 50 and transporting cam, has a cylindrical groove 225 for guiding a roller 226 secured to the end of a lever 221. The latter has a fulcrum 228 and is united with the end of an arm 220 forming a part of a segmental gear 230. The teeth of said gear 55 mesh with the teeth of a longitudinal rack 23| suitably guided in grooves or recesses of the machine table. Rotation of the cam 2|4 causes up and downward movement of the lever 221 whereby the segment 230 swings back and forth and effects 6o a corresponding reciprocating movement of the rack 23| Rigidly secured to the right-hand end of the rack 23| is a transporting magnet 232.v The latter has a coil 233 and a core provided with legs 234. The legs are fastened to a strut 65 235 which in turn is secured to the longitudinal rack 23| by screws 236. The legs 234 have end portions or lips 231 sli-ding in longitudinal grooves 238 and 238 (Figs. 2 and 2a) in the machine table. In Figs. l and 2 and in the diagrammatic view of 70 Fig. 3 the transporting mechanism is shown in the position in which a blank is being placed ready for the mechanism. From this position the magnet is moved to the right by the reciprocating movement of the rack 23| into a position for re- 75 ceiving another blank. The movement to the right-hand end position of the transporting magnet takes place while the swing arm of the feeding mechanism is swung from the stack towards the machine table. When the feed bell is swung onto the machine table the transporting magnet is in its right-hand end position, that is, to the right of the feed bell. In this position the lips 237 of the legs 234 of the magnet are disposed below the right-hand peripheral portion of the blank. After the blank has been correctly positioned by the locating mechanism the magnetl 233 is energized to hold the blank in fixed relation on its lips. Thereafter the locating plug is withdrawn from its engagement with the blank and the transporting rack 23| is moved to the left into the position indicated in the drawings. The coil 233 of the transporting magnet is connected to the main line 98 (Fig. 19) through the intermediary of a switch member 263B which is automatically opened and closed by a cam 24| fastene-d to a cam shaft 242 to which shaft is also fastened the cam 214. The cam shaft 242 is suitably supported on the machine frame. During a single revolution of the cam 24| the circuit of the transporting magnet is closed and opened once.

'Ihe operation of the transporting mechanism in relation to the operations of the mechanisms above described is indicated in the diagram of Fig. 18 in which a curve 243 indicates the operation of the magnet and a curve 244 indicates the operation of 'the longitudinal table feed, that is, the reciprocating movement of the rack 23| and the corresponding movements of segment 230 and cam 2I4. Asv curve 243 shows, the magnet is energized from about 358 degrees to about 54 degrees and deenergized from 54 degrees to about 358 degrees. The feed stroke, that is, the movement of the magnet towards the punch mechanism, begins at zero and ends at about 48 degrees. At the end ofthe feed stroke the magnet remains at rest until about 152 degrees of the i cycle, whence the return stroke begins, the magnet being returned into a position to receive another blank between about 152 degrees and 200 degrees of the cycle. As just pointed out, the feed stroke ends at about 48 degrees and the transporting magnet is deenergized at about 54 degrees, that is shortly after the termination o f the feed stroke.

As stated before, the transporting mechanism moves a blank located on the right-hand portion of the table to the punch mechanism which is arranged on a central portion of the frame. 'From a broad viewpoint, the`tra'nsporting mechanism represents a means for automatically feeding individual blanks to the punch mechanism. The latter, as will be more fully described in the following section, comorises a punch table which is continuously rotated. 'I'he transporting mechanism moves the blank into close proximity with the center of the rotating punch table so that the blank drops onto the rotating table as soon as the transporting magnet is deenergized. The locating of the blank onto the rotating table, more generally the engaging between the blank and the rotating table, is improved by the provision of push or hold-down buttons 245 and 245 (Fig. 3) secured to a frame 241 held on the lower end of a rod 248. The upper end of the rod is pivoted to a lever 249 having an intermediate point held on a fulcrum 250 (Fig. 1) and a left-hand end carrying a roller 25| bearing against a cam 252. The roller 25| is held in engagement with a lower cam surface of the cam 252 by a compression spring 253 (Fig. 1). The pins 245 and 24B are yieldingly supported on the frame 241 by the provision of springs 254 (Fig. 1). The lower cam surface of the cam 252 has a short notched portion 255, As soon as the roller 25| is permitted to drop into this notched portion, the push buttons 252 are forced downward by the action of the compression spring 253 to press the edge of a blank onto the stationary table. The magnetized lips at the opposite side of a blank ac- ,complish the same effect, that is, to hold the blank stationary against rotation until a centering mandril, more fully described hereafter, is properly entered in the blank. The downward movement of the push buttons 254 begins at about 50 degrees, and ltheir upward movement ends at about 65 degrees, as indicated by a curve 255 in Fig. 18.

The work stroke of the holding buttcns lasts for a short period of time only. The buttons force the blank down into engagement with the upper surface of the fixed plate adjacent the edges of the rotating punch table. The buttons are removed as soon as the blank is engaged by the mandril` and rotated therewith. A comparison between the curves 243 and 255 shows that the transporting magnet is deenergized immediately after the holding buttons have contacted with the blank.

It will be readily understood that the transporting of a, blank to the punch mechanism and the pushingl down of the blank by the push buttons takes place during a second cycle with respect to the handling of an individual blank by the machine as a whole. During the rst cycle, as stated before, the blank is fed to the machine table and located thereon. During the second cycle the same blank is being transported to the punch mechanism and, as will be described in the succeeding sections, the blankv is being punched during the second cycle and removed and discharged during a third cycle of operation. From this it will be seen that each` blank is manipulated or handled by the machine during three successive cycles. From another viewpoint, this means that three different blanks are being manipulated during each cycle. One blank is fed and located while another blank is transported and punched and a third blank is removed and discharged.

4. PUNCH MECHANISM The punch mechanism or punch press proper performs a plurality of consecutive punching, shearing, severing or deforming operations on each blank. In the present instance We have shown a punch mechanism for punching a plurality of uniformly spaced notches or openings into the periphery of an annular or circular disk lor blank. The punch mechanism according to our invention comprises a flying punch and die, that is, atool for carrying out the aforementioned operations of punching, shearing, severing or deforming. 'I'he term flying will best be understood by a brief consideration of the ordinary, known punch mechanisms.`

In these ordinary mechanisms a blank, for instance, a disk, is placed on a table, which lat,-

ter is rotated intermittently, Dur'ng a certain rest period of the table, a reciprocating punch `or male die performs a vertical stroke to punch certain period of time the punch performs another punching or working stroke. Thus the blank performs an intermittent motion with a rest period of a certain length between consecutive movements. These rest periods limit to a considerable extent the possibility of reducing the time for punching the entire blank. In this kind of punch mechanism the female die, usually arranged below the blank to be punched, is fixed,

remaining at rest. According to our invention the blank is move continuously.

In the case of an annular disk, such disk is rotated at a uniform speed. This is made possible by the provision of a punch and die which follow the movement of the blank while the punch acts yupon or penetrates the blank. Thus the punch The punch mechanism according to our invention, as best shown in Figs. 4 to 8 and Fig. l7 comprises a support 300 (Fig. 7) which forms a part of the frame and is disposed below the work table, and a casting 36| (Fig. 7) with lower flanges 302 secured to transverse recessed portions of the support 300 by means of bolts 303. The casting 30| may be moved in the grooves 302a to permit adjustment in accordance with the diameter of the annular blanks to be punched. The support 300 has an axial bore 304 for guiding a rotatable mandril. The mandril serves for rotating the blank to be punched and for securely holding the blank during rotationi/ The mandril comprises a cup-shaped, outer sleeve 305 which has an upper portion 306 resting on a shoulder 307 of the support 300. A gear 308 is secured to the lower end of the cup-shaped sleeve 305`by means of a key 309 and a nut 3|0. A ring 3|I is secured to the upper face of the upper portion 306 by means of screws 3|2. This ring `3|| forms a support or table for a blank to be punched. A blank 3|3 is indicated in Fig. 7 on the rotatable table 3||. The inner portion of the blank engages the table 3| and rotates therewith, whereas a circumferential portion of the blank slides on an annular portion 3 2a (Fig. 7) of the stationary table 26. y

As stated in the preceding section, the blank is transported to the punch mechanism by the transporting mechanism and held in position for a short time at the energized lips 237 of the transporting magnet and thereafter dropped onto the table by the action of the push buttons 245 and 246. The latter are withdrawn as soon as the blank engages the table 3| and rotates therewith. Means are provided for securely holding the blank on the rotatable table. These means comprise a holding plug and a key, connected to an actuating mechanism below the rotatable table, and a holding bell provided above said table.

The holding bell* comprises a cup-shaped body 3|4 held on a vertical shaft 3|5 (Fig. 4) b y means lof a nut 3|6. The body has a rim 3|7. A holding ring 3 8 is flexibly supported o-n the rim 3 |7 by the provision of four brackets 3|8a projecting through openings 3|c of the cup-shaped body.

This is accomplished `movement by the rotating table 3| The ring 3|8 is held by four bolts slidably arranged on the brackets, and forced downward by compression spring 3|8b. The shaftv 3|5 is guided in vertical guide bearings 3|9 and 320, which latter are suitably supported on the machine 5 frame. A grooved ring 32| (Figs. l and 3) is secured toI the upper' end of the shaft 3|5. The ring is engaged by pins 322 on a yoke 323 of a lever 324. An intermediate point of the latter is supported on a fulcrum 325 and the left-hand end 1o of the lever carries a roller 326 which slides in a cylindrical groove 327 of a cam. As clearly shown in Fig. 1, the cam defining the cylindrical groove or cam surface 327 also forms the cam surfaces 24| and 255 heretofore described. During rotal5 tion of the cam (Fig. 1) the cam surface 327 causes during a certain period of` a cycle the roller 326 to be moved upward whereby the lever 324 is turned clockwise and effects downward movement of the holding bell 3|4, whereby the 20 ring 3|8 of the bell is forced against the blank to 'securely press the same against the rotating table. During rotation of the blank the bell 3|4 rotates with the blank. The rotary movement of the holding bell is facilitated by the provision 25 of a thrust ball bearing 328 (Fig. 4) at the lower end of the shaft 3|5.

Relative rotary movement between the rotating table and the' blank is prevented by the provision of a key or key member 329 (Figs. 7 and 8) 30 engaging the key notch of the blank during rotation with the table. The key, as best shown in Fig. 8, has an intermediate portion 330 of prismatic shape and tapered end portions 33| and 332. The key is partly disposed in a plug 333 35 which has a conically shaped upper portion 334 with a slot 335, and a cylindrically shaped lower portion 336. Relative up or downward movement between the key and the plug. 333 is pre-y vented by a plate 337 secured to the top of the 40 conically shaped portion 334. The intermediate portion 329 of the key has a central recess 338 (Fig. 7) for receiving a lever 339, which latter turns at an intermediate point about a pivot 342. The function of the lever will be described later. 45 The end of the lever 339 is connected to the key by a pivot 340 projecting through a hole 34| in the intermediate portion 330 of the key. The plug 333 is disposed within a ring 350. The latter has two verticalI recesses 35| and 352 arranged in 50 alinement with the slot 335 of the tapered plug 333. The arrangement is such that the length of the base of the key is equal to the inner diameter of the ring 350 plus the radial depth of one of the recesses 35|, 352. Means including the 55 lever 339 are provided whereby either end 33| or 332 of the key is forced into one of the recesses 35| or 352. I

The ring 350 is held in the cup-shaped portion 306 of the sleeve 305 and prevented from upward As clearl'y shown in Fig. 7, the end face of the ring 350 abuts against the lower face ofthe table 3| The plug 333 for accommodating the key is secured to the upper end of an inner sleeve 353 by a, pin 354. This inner sleeve 353 is slidably arranged within the bore of the outer sleeve 305. The latter has a recess 355 and bearing surfaces 356 and 357 for the inner sleeve. The recess 355 is provided to reduce friction during relative axiall movements between the outer and inner sleeve. With this arrangement the inner sleeve may be moved up and down within the outer sleeve. Relative rotary movement between the two sleeves, however, is prevented by the provision of key means. These key means in the `present instance are defined by two lips 358 and 359 on the bearing surfaces 356 and 351 of the outer sleeve. The lips project into a vertical groove 360 of the inner sleeve. A grooved ring 36| is secured to the lower end of the inner sleeve 353 by a pin 362 (Fig. '7). This grooved ring is engaged by pins 353 secured to a yoke 364 (Fig. 3) on the right-hand end c-f a lever 365. The latter has an intermediate point supported on a fulcrum 366 and carries at its left-hand end a roller 361 disposed within a groove 368 of a cam 369. latter may be termed a punch-centering cam because it serves for raising and lowering the centering plug 333 with the key 329 for centering the blank on the rotatable table and holding it in fixed position during the punching operation. During operation, rotation of the punch-centering cam causes at a certain moment downward movement of the left-hand end of the lever 365 whereby the right-hand end thereof, that is, the yoke 364 with the pins 363, forces the ring 36| together with the inner sleeve 353 upward. This upward movement effects raising of the centering plug 333 with the key 329 until the lower end of the conical member 334 is disposed within the bore of the blank to be punched and one end 33| or 332 of the key is disposed within the key notch of such blank. If the key end 33| is disposed in the key notch of a blank, the other key end 332 is disposed in the slot 335 of the plug (Fig. '1).

'Ihe purpose of providing a key with two tapered ends 33| and 332 slidably arranged in the vslot 335 and connecting the key to the lever 339 is as follows: Let us assume that a blank is being punched with the lower portion of the end 33| of the key disposed within the notch of the blank. A complete cycle of the operation of the machine lasts 360 degrees. The punching operation of a blank obviously lasts less than 360 degrees of a complete cycle because such complete cycle also includes the feeding of a blank to the punch mechanism and the withdrawal of the punched .blank or work from the punch mechanism. The

feeding and the withdrawal in the present arrangement take place simultaneously and the arrangement is such that the feeding and withdrawal of a blank lasts one-third of a complete cycle. Hence, the punching lasts two-thirds of a cycle. During the actual punching operation, the rotatable table performs a complete revolution so that the key is in the same position as it was when the actual punching operation started. The punching now sets out for onethird' of the complete cycle, which is equal to one half of the actual punching cycle. -The punch table cr mandril, however, continues to rotate during this one-third of alcomplete cycle and at the end of this one-third of avcomplete cycle that is after the end of the blank transporting and withdrawal operation, the key is in a reversed position. The key end 33| which during the laforementioned cycle was located.

within the notch of a .blank is now located diametrcally opposite the key notch of a succeed-` ing blank to be punched. The other end 332 is located on the same side. However. it does not project outwardly from the conically shaped plug 333 and is not located vertically below the key notch of a succeeding blank.

Means are provided for reversing or repositioning the key, sliding it through the slot 335' of the plug 333 so that with respect to the next blank the other end 332 may be used as a keyfor holding the blank in position on .the rotating table,

The

From this viewpoint, the key 329 described above actually represents a double key with two key portions 33| and 332. Means are arranged whereby the key portion 33| is used for holding a blank and the key portion 332 is used for holding the succeeding blank. These means include the aforementioned lever 339 whichv may be termed a key-reversing lever. An abutment 310 is provided adjacent the lower spherically shaped end 31| of the lever 339. The abutment is adjustably secured to a link 312 (Fig. 3), which latter is fastened to a shaft 313 rotatably held A A lever 315 has its righton a fulcrum 314. hand end rigidly secured to the shaft 313 and its left-hand end provided with a roller 316 disposed adjacent a cam 311. The lever is normally pressed in downward direction by a tension spring 318 towardsan abutment 319. The cam 311 has a lip 380 on its outer surface. During a complete revolution of the cam 311 the lip 388 as it comes into engagement with the roller 311 forces the left hand end of the lever 315 upward, effecting rotation of the shaft 313 whereby the link 312 with the abutment 310 is turned to the rightiand moves the lever 339 into the position indicated in Fig. 7. As the roller 316 passes the lip 380 on the cam 311, the lever 315 is returned into its original position toward the stop 319 by the action of the tension spring 318. Fig. 7 indicates the moment at which the abutment 310 has been moved to the right to throw over the lever 339, effecting reversing of the key position. 'I'he abutment 310 thereafter is moved away from the spherical lever portion 31|. At the end of the actual punching, that is, after the blank has been rotated 360 degrees, the lever 339 with the ball 31| is again in the same position. The feeding of a blank to and the withdrawing of a punched or word blank from the punch mechanism takes place during another 180 degrees rotation of the rotating table, at the end of which the lever 339 with the ball 31| which rotate with the mandril are'in reverse position so that not the key end 33| but the key end 332 will be located on the notched side of the succeeding blank. The use of the key end 332 which is located within the slot of the plug 333 is made possible by reversing the key, as described above. Assuming that in the aforementioned operation the key end 33| while underneath the table was positioned within the slot 35| of the ring 353, in the succeeding operation with the key reversed, the end 332 will be positioned within the recess 352 of the ring 350. 'Ihe reversing operation of the key takes place during the transporting and withdrawal operation. The double key reversing arrangement permits the saving of time and may be provided whenever blanks are provided with an even number of notches.

The mechanism sofar described includes a rotatable table for supporting and rotating a blank, a bell and a centering plug with a key for holding a blank securely on the rotating table. The holding bell is moved onto the table and returned once during a cycle and the centering plug with the key is raised above the table and lowered also once during a cycle. In addition, the key member which is in the form of a double key is reversed once during each cycle whereby the two ends of the key member are alternately used for holding successive blanks. The raising and lowering of the bell and the centering plug with the key, and the reversing of the latter is effected by three cams on the cam shaft 242.

The movement of the homing bell 3M is indicated by a curve 38| in the diagram of Fig. 18. The bell begins to move downward at about 54 degrees of a cycle and reaches its lower end position in which the flexibly supported holding ring 3|8 engages the blank at about 74 degrees of the together with the centering plug is indicated by a curveI 3,82. Upward movement of the double key and the plug which form a part of the mandril begins at about 54 degrees, that is, simultaneously with the downward movement of thev holding bell. The double key and the centering plug are lowered at about 340 degrees, reaching its lower dead-end position at about 360 degrees, that is, at the instant at which the holding bell reaches its upper end position.

The ying punching tool comprises a punch or male member 400 (Fig. 17) and a female member or die 40|. Thal-die is in the form of a rectangular plate which has an opening 402 in a central portion thereof for receiving a lower por vtion 402e (Fig. 4) of the male member 400. A

rear portion of the die has a recess 403 'and a plurality of bores 404 and a key notch 405. The

lower surface of the plate isprovided with another key notch 406 (Fig. 4). The female mem.- her, hereafter termed die is secured to an oscillating carriage 401. The latter, as clearly indicated in Fig. 17, is in the form of a rectangular .frame which has a rear portion provided with ears 408 and a base portion 409 to which the die 40| is secured by means of screws 4|0. An opening 4|| in the base portion 408 is in alinement with the opening 402 of the die and a notch 4|2 of the base portion is in alinement with the notch 406 in the die 40| (Fig. 4). Relative movement between the die 40| and the base 409 is prevented.

by a key 4|3 located in the notch 4I2 of the base and the notch 406 of the die. 'A guide 4|4 for the punch 400 is secured to the die 40| and the carriage 401. The guide 4| 4 (Fig. 17) has a strut 4|5 provided with a projection 4| 6 fitted into the recess 403 'of the die. project through the ends' of the strut '415 and thereby secure the guide to the die 40|' and to the base 409 of the carriage 401.

The punch 400 has a. sliding fit in a channel 4|6 of the guide 4|4. The punch 400 is held on a crosshead 4I1 by a dove-tail connection between a lower end 4|8 (Fig. 4) of the crosshead and an' upper end 4|9 (Fig. 17) of the punch. The connection between the crosshead and the punch is such that the punch is prevented from moving up or down relatively to the crosshead but is permitted to move sidewse', more specifically to perform a swinging motion with respect to the crosshead about the center of the rotary punch table. As best shown in Fig. 4, the dovetail connection between the punch and the crosshead denes clearances 420 to permit such rela" tive swinging or flying motion between the punch `and the crosshead. The crosshead is movably arranged between guides 42| (Fig. 7) and supported through the intermediary of a. bushing 42| on an eccentric 422 of a punch shaft 423.

The screws 4|0 l Rotation of the punch shaft 423 effects a reciprocating motion of the punch, that is, causes the punch to move up and down. The punch shaft 423 is driven through the intermediary of a universal coupling 424 from a drive shaft 425 (Fig. 4:). The punch shaft is continuously operated, that is, while the actual punching takes place, which, as pointed out above, takes about twothirds of a complete cycle as well as during the other third of this cycle while the punched blank is withdrawn from and a new blank is transported to the punch mechansm. This is made possible by the provision of means for lowering and raising the punch shaft so that with the lowered punch shaft the punch penetrates the blank and enters the die, whereas with the punch shaft raised, the punch merely reciprocates without reaching down to the blank and die. The means for lowering and raising the punch shaft once during a complete cycle comprises two eccentric sleeves or bushngs 426 and 421, (Fig. 4), one on each side of the eccentric 422. The two ends of thev punch shaft 423 are rotatably held in the eccentric sleeves 426 and 421 through the intermediary of bearing bushings 428 and 428 respectively. The eccentric bushings'428 and 421 are supported on bearings 430 and 43|. A gear 432 is secured to the left-hand end of the eccentric bushing 426 and another gear 433 is secured to the right-hand end of the eccentric bushing 421,

-The gears 432 and 433 mesh with gears 434 and tioned bearings 430 and 43| forthe eccentric bushings 426 and 421 respectively. A gear segment 439 is secured to-an intermediate portion of the punch raising and lowering shaft 438.

The gear segment 439 meshes with a gear segment 440. The segment 440 forms the right-- hand end of an'arm 44| (Figs. 1 and 3) which is connected to a fulcrum 442 and whose lefthand end carries a roller 443 sliding in a cylindrical groove 444 of a cam. This cam with respect to-its function may be termed a raising and lowering cam. During a complete rotation of the cam the roller 443 is raised and lowered once to effect lowering and raising respectively of theA punch shaft.` The punch shaft in Fig. 4 is indicated in its raised position. Rotation ofthe gear segment 430' by the action of the segment 440 and the raising and lowering cam effects rotation of thegears 434 and 435,

resulting in turning movement of the gears 432 and 433. The latter thereby turn the eccentric bushings and thus lower the punch shaft 423 The lowering and raising of the punch shaft 423 with respect to the drive shaft 425 is possible by the provision of the coupling 424. In the present instance this coupling has been indicatedas a universal coupling known' as a modied Oldham coupling. It comprises a plurality of disks 445 (Fig. 6). Each'disk has a lip 446 projecting into a diametric recess 441 of an adjacent disk. This coupling permits driving of the punch shaft by the drive shaft while the axes of the two shafts are out of alinement. f

The punch shaft effects reciprocating movement, that is, up and downward movement of the punch. The swinging or flying yor oscillating movement of the punch is effected by the carrlage 401 through the intermediary of the punch guide 4|4. A'I'he carriage 401 (Fig. 17) has a rectangular opening 450 which is centered on the mandril, more specically the outer surface of the cup-shaped portion 306 (Fig. 7) through the intermediary of a square bushing 45| which has side walls engaging side walls 452 dening the opening 450 of the carriage. The bushing has a bore 453 forming a bearing surface for the cup-shaped portion 306 of the mandril. A cylindrical projection 454 of the bushing 45| is seated on an annular shoulder 455 of the base 300. The carriage is secured to the square bushing 45| by adjustable means comprising a bolt or screw 456 and nuts 451 and 458 (Figs. 4 and 17). This adjustment permits different punching operations for blanks of different diameters. The rear end of the carriage, that is, the ears 408, are connected to a mechanism for oscillating .the carriage. The oscillating or swinging movement of the carriage is effected by an oscillating cam 460 which has a cylindrical, at least partly helically shaped, groove 46| and is secured to the drive shaft 425 (Fig. 4). Rotary movement of the cam is transmitted to the oscillating carriage by means comprising a roller 462 riding in the cam groove 46| (Fig. 5) and being secured to an arm 463 of a bell cranklever 464. 'I'he bell crank lever is connected to a fulcrum 465. Another arm 466 (Fig. 17) of the bell crank lever is adjustably secured toone end of a link 461 by means of a nut and a washer 468. The other end of the link 461 is secured to one end of an adjustable eye bolt 469 by a nut 410, andV the other end of the eye bolt 469 is secured to the ears 408 of the carriage by a pin 41|.

During operation, rotation of the oscillating cam 460 causes the bell crank lever 464 to swing about its fulcrum 465 (Fig. 5), resulting in oscillatory movement of the carriage and its square bushing about the cup-shaped portion 306 of the mandril, The carriage is continuously oscillated. The number of oscillations of the carriage is equal to the number of strokes of the punch.

. The speed of the oscillatory movement in at least one direction is equal to the speed of the rotary movement of the mandril so that no relative rotary movement takes place bet-Ween the punch, the die and the rotating blank during the working stroke of the punch. This constant speed movement is accomplished by the helical shape of at least a portion of the groove 46| in the cam 460. After the working stroke, that is during the return stroke of the punch, the carriage i s moved back into a new or original position. The speed of the backward movement is independent of the rotary speed of the table.

The punch mechanism also includes means for stripping the punch, more specifically the portion 402a of the punch or punch proper which engages the blank to be punched. The stripping means comprises a stripper 480 (Figs. 4 and 17) which has a horizontal plate 48| disposed intermediate the lower face of the guide 4|4 and the .blank to be punched. 'I'he plate 48| has an opening 482 fitting the punch to strip the blank from the punch during its return stroke as the punch has a tendency to stick to the blank. The plate 48| is integrally formed with an upright 483 (Fig. 17). The upright is disposed within a groove 484 of the punch guide 4|4. The upper end of the upright 483 (Fig. 17) is united with a U-shaped member 4 85 for supporting' 'the stripper on a bar 486, which latter is secured on a lip 481 of a ring 488. The ring 488 is held on a recessed end portion of the eccentric bushing 421 (Fig. 4). The recessed end portion is concentric with the punch shaft. T he arrangement is such that the stripper may be adjusted, that is, moved towards and from the lower face of the guide member 4| 4. To this end the bar 485 is provided with a bore 489 for accommodating a worm 490 eccentrically secured to a pin 49|. The pin 49| is secured to the lip 481 by a nut 492. The bar 486 has another bore 493 transverse to the bore 489 for accommodating an adjusting screw 494. For adjusting the stripper the nut 492 is loosened. Thereafter the screw 494 is turned to effect turning movement of the eccentric worm 490, whereby the stripper is moved in vertical direction. The adjustment is especially desirable where blanks of different thicknesses have to be punched.

The mechanism as shown in the drawings is adjustable to permit punching of blanks with diierent diameters. For punching a blank of a certain diameter, the punch is located'at a certain radial .distance from the center line of the mandril, In order to punch disks of greater d1- ameter or, from another viewpoint, to punch holes into a blank at a greater radial distance from the center line of the mandril, the punch mechanism has to be moved to the right in the View of Fig. 4 and at the same time the adjustment of the carriage on the square bushing surrounding the mandril has to be changed. The movement of the punch mechanism to the right in Fig. 4 isvfacilitated by the provision of a special shaft 425. This shaft, as indicated in Fig. 4a, is splined comprising two halves 495 and 496, the half 495 of which has a projection 491 projecting into a iametrical slot 498 of the half 496, an arrangement known as spline shaft. To permit a sufficient amount of transverse movement of the punch mechanism, the gear segment 440 (Fig. 2)

is provided with wide face teeth, wider than the teeth of the segment 439 for raising and lowering the punch shaft. All that is necessaryto adjust the punch mechanism in transvese direction is to loosen the bolts 456 for centering the carriage on the mandril, and the lbolts 303 holding the casting '30| on the support 300 and to move the casting 30| along the grooves 302a into the delowering and raising the punch shaft 423. The

lowering of the punch shaft, that is, the turning of the eccentric bushing begins at about l74 degrees and the bushing reaches its lower ydead-end position at about degees. The bushing is raised at Labout 325 degrees, reaching its upper dead-end position at about 350 degrees. The curve 502 indicates the movement of the punch.

yIt clearly shows that the punch is reciprocated continuously. The reciprocation takes place in two levels in accordance with the positioning of the eccentric bushing. The punch reaches its lower level at about 85 degrees, that is, simultaneously with the reaching of the lower dead` Y end position by the eccentric bushing and the punch is moved towards its upper lcvel atabcut 325 degrees, reaching its upper level at about 350 degrees, that is, simultaneously with the reaching of the upper dead-end positionby the :scentric bushing.` V

The relation between the reciprocating move- 

